FI87094C - PRESSVALS FOER BEHANDLING AV EN BANDFORMIG PRODUKT - Google Patents

Description

87094 "PRESS ROLLER FOR HANDLING GOODS" - "FRESSVALS FOR BEHANDLING AV EN BANDFORMIG PRODUKT"

The invention relates to a press roll which functions to process a web-shaped article, in particular to remove water from the fibrous web and forms a press gap with the counter roll, in accordance with the features given in the main concept (parts a to e) of claim 1.

Such a press roll is known from DE-OS 35 01 635 (= US-PS 4,625, 376). The known press rolls, as well as the subject of the present invention, have two different construction methods. In one construction, the support body, which extends through the rotating press jacket, is fixed. In another construction, this support frame is rotatably mounted like a compression sheath.

In the case of a fixed, i.e. non-rotating, support body, then the flexible compression sheath slides in the region of the compression gap over the support body when this compresses the compression sheath against the counter roll. For this purpose, it is advantageous to place (according to DE-OS 33 11 996 = US-PS 4,555,305) a radially movable pressing shoe on the support frame, over which the pressing ... the diaper slides. The sliding surface of the press shoe is always shaped to be hard to counteract the curvature of the counter roll, so that the press gap has a certain dimension in the direction of web travel, i. a surface-like compression gap is formed.

; ; In this case, the cross-sectional shape of the support body can be arbitrary, e.g. rectangular, tubular or I-shaped.

If the support body is rotatably mounted and has a circular cylindrical roller body, then the support body rotates when it compresses. against the counter roll, in the region of the nip inside the nip.

In both embodiments, the press jacket of the known press roll is always formed in a liquid-tight manner. For the inner surface of the press jacket must always be provided with a lubricant, so that nothing of the lubricant can penetrate out of the interior of the press roll. Otherwise there is a risk of the web being treated becoming dirty.

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For these reasons, it is also very important that the ends of the compression jacket are absolutely fluid-tight connected to both (rotatably supported frame bearings) jacket support elements. In addition, it is important that this connection can be made and removed again in a short time. After the specified service life, it must be taken into account that the compression jacket must be replaced with a new compression jacket. When installing the press roll on a paper machine, for example, it must be taken into account that the press jacket must be replaced in the shortest possible time, reducing the machine's downtime as much as possible.

In general, as with the press roll according to the invention, the press jacket preferably has a disproportionately hardened reinforcing material, e.g. polyurethane. The reinforcement is preferably a tissue.

The measures of the known press roll for fluid-tight connection of the ends of the press jacket to the support element of the jacket have proved to be good in practice. However, it is often still difficult to carry out the attachment of a new compression jacket to the jacket support elements in the shortest possible time. This installation method must also ensure that the ends of the compression jacket are centered as closely as possible on the jacket support elements. For this depends on whether the pressure jacket rotates smoothly in use.

The object of the invention is therefore to improve the press roll mentioned at the beginning in the direction that the centering and attachment of the ends of the press jacket to the support elements of the jacket can be carried out even more reliably and faster than hitherto.

This object is solved by the characteristic feature of claim 1. Other possible improvements in the layout of the task are given in the subclaims.

The advantages of the invention will be described by way of an embodiment shown in the following drawing.

Figure 1 shows a radial partial section of the end of a press roll having a fixed support body and a jacket support plate, in line I-I of Figure 2.

Figure 2 shows a sector of the shell of the support plate, seen in the direction of the arrow in Figure 1.

Figure 3 shows the compression sheath alone in oblique view.

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Figure 4 shows the intermediate stage of the installation of the compression punches shown in Figures I and 2.

Figure 5 shows an example with a rotating support body and a jacket support ring.

The press roll shown in Figures 2 and 2 has a non-inclined support body 24, both ends (only one of which are visible) supported on bearing brackets 25 by bearing pins 24a. The outer surface has a recess 246 in a known manner with a press shoe 26 corresponding approximately to the length of the paper web to be processed. . An endless, tubular compression jacket 10 rotates around the press shoe 26 of the support body 24. By supplying the pressure medium, the press shoe 26 can press the press jacket 10 against the counter roll (omitted in the drawing).

At each shaft end there is an axially movable but not rotating bearing ring 11 placed on the bearing pin 24a. A bearing support plate 12 is mounted on the bearing ring li by means of a rolling bearing 13. A radially inwardly turned clamping edge 16 of the compression sleeve 10 is fixed to the end side of this housing support plate 12. To facilitate installation, the clamping flange 15 can be divided into easy-to-handle segments. In addition, the segments may have noses 17 that fit into the annular groove 18 of the sheath support plate 12.

To seal outwardly the interior of the press roll bounded by the press jacket 10 and the jacket support plates 12, the following exists: the press jacket 10 consists of a substantially liquid-tight synthetic material, e.g. polyurethane; it is preferable to reinforce it with a support fabric assembled in a known manner from circumferential and longitudinal yarns. The outer end side of the sheath support plate 12 and the edge zone of the compression sheath 10 together form a pair of sealing surfaces, the width of which is indicated by S in Fig. 1. To ensure tightness with even greater certainty, the jacket support plate can be provided with an annular groove and an O-ring 23. Finally, on the outer side of the rolling bearing 13 there is a shaft sealing ring 19 resting in a housing ring 20 attached to the jacket support plate.

To tension the compression sheath 10 axially, tension springs 21 are tensioned between the support body 24 and the flange 14 of the bearing ring 11. To facilitate installation of the compression sheath 10, the bearing bracket 25 has at least one pressure screw 22 by means of transiently pressing the bearing ring 11 together with the sheath support plate 12 .

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Figure 3 shows the situation of the compression sheath 10 before it is pulled over the support body 24. It then has an elongate approximately cylindrical basic shape. Numerous approximately triangular sections 29 have been machined at both ends, leaving approximately trapezoidal tongues 28 parallel to the axis. However, instead of trapezoidal tongues, rectangular tongues can also be made. To simplify the drawing, the compression jacket is shown in Figure 3 (in oblique view) as a circular cylinder. In reality, its cross-section, due to the flexibility of the material, will more or less deviate from the circular shape. The compression side of the inner periphery of the shell length (corresponding to Figure 3 the inner diameter d) is selected so large that the distance between the generated prescribed clamping the shell and the support frame 24. In addition, the outer diameter of the sheath support rings 12 is always selected to be slightly smaller than the inner diameter d of the compression sheath 10. Thus, the compression sheath 10 can be pulled with only a small force over the support body 24 and the support rings 12 of the sheath.

The length L of the part free of the recesses 29 of the compression jacket is determined by the approximate distance A (Fig. 1) between the outer end surfaces of the jacket support plates 12 and the width B of the sealing surfaces. The length z (and thus the total length G) of the tongues 28 of the compression sheath 10 is chosen so that the tongues ·; 28 extend radially inwardly over the clamping flange 15 in the pre-assembled situation of the clamping jacket. In other words: it is ensured that the distance s from the center line of the press roll axis to the ends of the tongues 28 is smaller than the distance r from the center line of the press roll axis in the radial direction of the tightening flange 15 to the inner edge. (Figure 2).

Conversion of the compression jacket 10 from the elongate shape shown in Figure 3 to the shape of Figures 1 and 2, in which the edge zones of the compression jacket part of length L extend inwards like a flange and form a flat sealing surface, is performed as follows:

The clamping flange segments 15 are either completely removed or placed as far apart as possible from the sheath support plates 12. The tongue 28 (or two pairs of radially opposite tongues in each case) is turned radially inwardly around the rounded outer edge 12a of the sheath support plate 12. The tip of each tongue 28 has a hole 31. In addition, there is a bolt (or cylinder surface 30) in the sheath support plate 12 for each tongue in the radial direction inside the screws 16 (i.e. in the area between the screws 16 and the centerline of the press roll). Here, approximately 8 87094 (or slightly oblique to the center line) is inserted axially from the outer end face of the sheath support plate 12? out. It is advantageous to insert each tongue 28 onto one such cylindrical surface 30. Thus, through a large number of tongues, the numerous tensile forces in the edge region of the press jacket act so that the bent sealing surface width B shown in Figure 1 is pressed circumferentially, while always slightly bulging outwards. .

As can be seen from Figure 2, on the outer end side of the sheath support plate 12, a bolt-shaped projection 27 is always placed between the two screws 16. The total number of bolts 27 of the screws 16] a is equal to the number of tongues 28 or recesses 29. The arrangement of the screws 16 and the bolts 27 is chosen so that they fit exactly into the recesses 29. It is preferable to place the screws 16 and the bolts 27 on the same sub-circle so that the depth z (Fig. 3) can be made equal in all sections. However, this can also be deviated from. It is also preferred, as shown in Figure 2, that there be an equal number of screws 16 and bolts 27 and these are distributed alternately around the circumference. In addition, it is convenient to place a sleeve 32 in each of the threaded bores for the screws 16 and to make the outer diameter of the sleeves 31 and the bolts 27 the same; thus, all the recesses 29 of the compression sheath 10 can be shaped to be identical.

In the above-described change of the edge area of the clamping sheath 10, the tongues • 28 are pulled in the direction of the center line of the shaft until the bottom 9 of the recesses 29 (Fig. 3) reaches the bolts 27 and sleeves 31. This very quickly When • all the tongues have been placed on the cylinder surfaces 30, the edge zone of the clamping jacket 10 is pressed between the jacket support plate 12 and the tightening flange 15 (by tightening the screws 16). Finally, the pressure screw 22 is removed from the bearing ring 11 so that the compression springs 21 can tension the compression sheath 10 in the axial direction.

Figure 4 shows how each of the tongues 28 can be tightened by means of a tubular tool 33 in the axial direction of the press roll. A jacket support plate 32 with sealing rings 23, sleeves 32 and cylinder surfaces 30 is shown. The tension flange segments 15 and screws 16 have been removed. The tool 33 is inserted through 31 and the printed surface of the cylinder 30. The tool 33 can reverse the direction of the arrow P direction of the roll shaft and then pushes the tongue 28 of the cylinder surface 30 of the hole 28 at the tip of the tongue.

This method has various advantages over the prior art described in DE-OS 35 01 635:

Tension springs are no longer required, which have so far had to be removed after installation. Installation can take less time; moreover, it leads with greater certainty than hitherto to the precise centering of the compression sheath.

Figure 5 shows the use of the invention in its entirety on a rotary press roll having the above-described press jacket 10 as a loose coating. Unlike other embodiments, the support body is now formed into a rotatably mounted and therefore circular cylindrical roll body 44, the pin 44a of which may be used. The basic shape of the compression sheath 10 is the same as shown in Fig. 3. The compression sheath 10 bounded by the interior front side liquid-tight connection could in principle shaped as in Figures 1 and 2, i.e. with a pin 44a transferred to the bearing ring 11 and the bearing shell supporting plate 12. In contrast, formed in Figure 5, the bearing ring 51 of the roll frame 44. This is (rolling bearing 43 and the seal ring 49) a bearing annular jacket support element 42 (centrally with respect to the roll body 44). A clamping sheath 10 is fastened to the outer end surface of the sheath support element 42 by means of a flange 45 and screws 16 '. This attachment and the above shaping of the compression sheath 10 take place in the same manner as described above in connection with Figures 1-4.

To center the compression jacket 10, sleeves 32 'exist as shown in Fig. 1, however, these are inserted into the clamping flange 45 as shown in Fig. 5. Likewise, the cylindrical surfaces 30' tightening the tongues 28 ', in contrast to Fig. The tongues 28 'extend slightly further in the direction of the roll axis than in Figure 1. Thus, it is possible for each tongue to be provided with two holes 31 and 34. The opening 34 at the tip of the tongue can be gripped by a tool resting on the inner jacket surface 35. in the axial direction until the tongue can be placed on the cylinder surface 30 'by the second inner hole 31. It will be appreciated that this method is also useful in the structure shown in Figures 1 and 2 with a fixed support frame.

Figure 5 shows a small part of the counter roll 50 which forms a compression gap with the press roll. Outside the nip, there is a small gap a between the nip 10 and the roll body 44, because the inner diameter d of the nip 10 (Fig. 3) is larger than the outer diameter of the roll 44. Axial tightening of the compression sheath 10 is not required in Figure 6. However, if necessary, provision could be made for axial displacement of the bearing ring 51 relative to the roller body 44.

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The roller body 44 may be made of metal alone, i.e. without the hitherto very necessary solid coating, e.g. rubber, artificial or the like. Its function now takes on a detachable press jacket rotating with the roll body 10. But on the other hand, it is also possible, in order to achieve special effects (as the web to be treated passes through the press slot), to further provide the roll body 44 with a solid coating 48, as shown in Figure 5. In this case, there are many variations by selecting certain pairs of materials for the compression sheath 10 and the solid coating 48.

Necessary pipes for the import and export of lubricating and / or cooling fluid (eg for cooling the roller body) have always been omitted from all figures. The compression sheath 10 the inside of the lubricant, especially a compression slot passageway, a fixed support frame 24, 26 (Figure l) where necessary; but it may also be appropriate with a rotating support frame (Figure 5). However, if in the case of Fig. 5 such lubrication of the compression jacket is omitted, then the liquid-tight sealing of the interior is very advantageous, since penetration into the water and thus corrosion is prevented.

Claims (4)

87Cv'- A press roll which acts to process a web-shaped article, mostly to remove water from the fibrous web and together with the counter roll, forms a press gap, having the following characteristics: a) a solid or rotating press extending through the endless, flexible and liquid-tight press jacket (10)! a bearing support frame (24; 44); b) a jacket support element (plate 12, ring 42 or the like) is rotatably mounted on each roll end; c) an edge zone of the pressing jacket (10) extending radially inwards to each end of the roll outside the pressing slot on the end side of the jacket support element (12; 42), the edge zone having an annular sealing surface B on the end side which can be tightened by a tightening flange 45; to the sheath support element; d) at each end of the roll, a plurality of tongues (28) extending in the direction of the axis of the roll are formed at regular intervals on the periphery of the press roll in the edge zone forming said sealing surface (B), so that there is a recess (29) between the two tongues; e) in the region of the outer end side of the jacket support element (12; 42) there are radially inside centering elements (e.g. screws 16, bolts 27, nipples and the like) arranged radially inside the sealing surface (B) on the circumference and at the same time in the recesses (29) the base (9) of one part of the recesses (79) for centering the compression sheath (10) rests on one of the projections (16, 27); f) characterized in that inside the centering elements (16, 27) in the radial direction there is a rigid retaining element (30, 30 ') for at least part of the tongues (28; 28 *) of the clamping sheath (10), which keeps the tongue at a certain distance from the center line. Press roll according to claim 1, characterized in that the individual retaining element (30; 30 ') is formed as a protruding surface, bolt or the like from the outer end surface (or the inner end surface of the clamping flange 15) of the jacket support element (12) and that the individual tongue (28; 28 ') is a suitable opening (31) for this. Press roll according to Claim 2, characterized in that the retaining element (30; 30 ') is arranged inclined towards the center line of rotation of the press roll. I: 9 8 7 4ν 4 Press roll according to one of Claims 1 to 3, characterized in that the radial distances between the centering elements (16, 27) and the retaining elements (30) on the one hand and the bottom (9) of the recesses (29) and the opening in each tongue (28) on the other (31) is selected so that the base (9) rests on the centering element (16, 27) when tightened. 10 8 7 ϋ 9 £